Fluid pump



Oct. 16, 1951 w, c, Ack N 2,511,711

FLUID PUMP 7 Filed Jan. 23, 1948 TU MIIITIJR INVENTOR.

William E Harzkman ATTORNEYS.

Damn

Patented Oct. 16,1951

UNITED STATES PATENT OFFICE 4 Claims.

This invention relates to fluid pumps.

The primary object of this invention is the provision of a compact economically constructed and operated fluid pump capable of delivering fluids under high pressure.

A further object of this invention is the provision of an improved multiple pressure stage fluid A further object of this invention is the provision of an improved fluid pump having a novel impeller blade arrangement capable of appreciably increasing pressure of a fluid over inlet pressure without creating excessive centrifugal action.

A further object of this invention is the provision of an improved set of propeller blades for the rotor portion of a pump having small throw action compared to conventional centrifugal pumps, but capable of efficiently delivering the fluid at high pressures.

Other objects and advantages of the invention will be apparent from the following detailed description.

In the accompanying drawing, forming a part of this specification, and wherein similar reference characters designate corresponding parts thruout the several views Figure 1 is a top elevation of the pump.

Figure 2 is a vertical cross sectional view taken thru the pump in the plane of the drive shaft axis.

Figure 3 is a transverse cross sectional view taken thru the pump substantially on the line 33 of Figure 1.

In the drawing, wherein similar reference characters designate corresponding parts thruout the several views, the letter A may generally designate the pump. It consists of a casing structure B having a rotor C mounted therein upon bearings D, and driven by a shaft E which may receive its source of power from a motor (not shown) connected by a pulley and belt or chain arrangement F thereto.

The casing structure B preferably includes side walls H! and H. The latter has a substantially cylindrical-shaped wall l2 integrally connected therewith defining a fluid compartment I3 wherein the impeller structure is mounted. The wall I2 is detaohably connected at M to the wall Ill.

The wall structure I is provided with a hub extension I4 having a fluid inlet opening |5 axially of the casing. The cylindrical wall l2 has a tangential extension 20 thereon providinga delivery passageway 2|.

A hub extension 22 is provided upon the wall II. It receives the drive shaft E which is supported in suitable bearings D of any approved nature, encased within packing material 25. The

outer wall 26 of the hub may be detachable.

Pressure sealing structures K are used at each side of the rotor, supported in the hubs I4 and-22. Each of these pressure seals includes telescoping portions 30 and 3| having flanges at their outer peripheral portions and receiving therebetween a resilient sealing sleeve 32 which is urged at its ends by a spring 33 into engagement with the flanged portions of the telescoping parts 30 and 3|. The spring urges the part 3!] outwardly into the hub and the part 3| inwardly against the wall of the rotor, as shown in Figure 2. The pressure seals are conventional and need not further be described except in their specific relation to the casing structure and rotor of the pump.

The rotor C consists of circular disc-shaped walls 4|] and 4|. The former has an'opening 42 therein for axial inlet of the fluid to the rotor, and the Wall 4| receives the end of the shaft E in keyed relation therewith. The outer peripheral margins of the walls are spaced slightly from the inner periphery of the stator wall I2, as shown.

The rotor is provided with a plurality of sets of impeller blades. In the present example three sets 50, 5| and 52 are shown, arranged from the center outwardly. In the main, the sets of blades are the same, with the exception of the outer set which'difiers slightly as will hereinafter be mentioned.

It is the purpose of this invention to provide a multiple stage development of pressure; each stage increasing the pressure over inlet pressure without appreciable centrifugal turbulence of the fluid or liquid. To that end I prefer to provide each impeller set with four blades; 60, BI, 62 and 63 for the inner set; 68*, fil 62 and 63 for the intermediate set, and 6 l 62 and 63 for the outer set. The inner wall surfaces of the rotor plates 40 and 4| are grooved to receive the impeller blades in sealed relation. Each impeller blade is struck from a single center. It does not have a compound curvature. The blades 60, 60 and 60 are struck from a center 10 located a predetermined distance from the axis H of the rotor. The blades 6| 6| and 6 I are struck from a center 12 arranged away from the center 10 and spaced the same distance from the axis ll as the center 10. The blades 62, 62 and 62 are struck from a center 13 arranged 90 from the center 12 and the same distance from the axis center H as the center I2- and diametrically oppose the center H with respect to the center 10. The blades 63, 63 and 63 are struck from a center 14 which is 90 away from the center 13 and the same distance as the center 13 from the center H, and diametrically opposite the center 12 with respect to rotor center H Intersecting lines thru the centers (-13 and thru the centers 14- 12 are at right angles.

Referring, to therelation of the blades of each impeller set; said: blades; each extend thru an arc of approximately 135. The inner ends of the blades are flared to a chisel edge lying on an imaginary circle Bil which intersects all of the chisel edges of the inner ends of said blades. It is thus apparent that inasmuch as the blades are symmetrically arranged, the inner end of each blade overlaps approximately 45 with the outer end of its complementary adjacent blade. This overlapping defines four fluid passageways designated at 90 which gradually tapers along the path of the passageway in convergence towards the outlet end 90 This is a characteristic construction of the liquid passageways of each set of impeller blades 50, 5! and 52. The forward or inner ends of complementary blades of each impeller blade set all lie in the same straight line intersecting the axis of the rotor, as will be noted from the drawing.

It is to be noted that the distance of the blade centers from the rotor axis is relatively smaller. Of course this determines the throw of each blade, which is also relatively small compared to conventional centrifugal pumps, and this feature eliminates violent turbulence of the fluid whose pressure is to be elevated. There is an annular free space I00 between the inner and intermediate impeller sets, and an annular space Ill] between the intermediate and outer impeller sets into which the fluid is delivered.

Constricting the liquid passageway 98 from its inlet end to its outlet end et tends to eliminate back pressure upon the fluid delivered from the blades.

The blades of impeller set 52 are preferably outturned or flared at I05 at an angle of approximately 45 to the radial line from which the blade is struck. This tends to create a vacuum close to the discharge end 93 of the liquid passageway and assists in eliminating back pressure. Likewise, this flaring end tends to centrifu-- gally throw the liquid beyond the outer impeller set into the tangential discharge passageway 2i, without releasing pressure.

While I do not wish to be limited to the specific example herein set forth, in one small and cornpact multiple stage pump possessing the above characteristics, with an inlet water pressure of 45-1bs. per square inch, the first impeller set 59 elevated the pressure in the passageway I09 to 95 lbs. per square inch, and the second set of impeller blades 5! elevated the pressure of the liquid in the passageway NH to 150 lbs. per square inch. The delivery pressure of the liquid is further elevated by the third set of impeller blades 52 and leaves the discharge opening 2| at a pressure of 200 lbs. per square inch.

Due to the 135 length of the individual blades in the arrangement above described, it will be noted that the discharge end 98 of the liquid passageway opens into the annular space N30 or NH, as the case may be, in advance of the inlet end of the liquid passageway 90 of the next outermost impeller set; the degree distance between the discharge end of the liquid passageway of the inner set and the inlet end of the adjacent 4 rear liquid passageway of the next outermost set being 45.

Various changes in the shape, size and arrangement of parts may be made to the form of invention herein shown and described without departing from the spirit of the invention or the scope of the claims.

I claim:

1. A. fluid. pump comprising a stationary casing having a fluid compartment therein provided with an axial fluid inlet opening and an outer fluid delivery exit, and a single rotor supported by the casing having an impeller structure of multiple blade sets within the compartment, all of which are disposed in the same plane normal to the axis of the rotor, each set comprising a plurality of blades eccentrically positioned in the casing with respect to the axis of rotation of the rotor and having relatively shallow fluid-throw with the outer ends of each blade overlapping and radially spaced from the inner ends of the next rear adjacent blade to define liquid passageways, each set of blades being spaced from its adjacent sets of blades by an unobstructed annular passageway, the blades of the sets being so arranged that the discharge end of the liquid passageway between overlapping blades of one set is appreciably in advance of the inlet end of the liquid passageway between blades of the next outermost set of blades.

2. A high pressure fluid pump comprising a stationary casing having an axial fluid inlet opening and an outer substantially tangential fluid delivery exit, a rotor supported by said casing, and a pressure developing multiple stage blade structure supported by said rotor within the compartment, comprising a plurality of radially spaced sets of blades, each set of blades comprising aplurality of, curved blades struck from centers eccentric to the axis of rotation of the rotor with the inner ends of the blades of each set radially overlapping the outer ends of adjacent blades to define liquid discharge passageways, the impeller sets each having the same number of blades, with. a blade in each set struck from a common center and arranged in substantially the same relative position radially from the axis of the rotor.

3.. A fluid pump comprising a stationary casing'having a fluid chamber therein provided with an axial fluid inlet opening and an outer fluid delivery exit opening, a rotor supported by the casing having fixedly connected therewith an impeller structure provided with multiple blade sets, all of which are disposed in said casing chamber and connected together for rotation in the same direction in said chamber, said sets of blades all being located in the same plane normal to the axis of the rotor, each of said sets comprising a plurality of blades each blade of which is eccentrically positioned in the casing with respect to the center of rotation of the rotor and has a shallow fluid throw, the outer end of each blade of each set being spaced from the inner end of an adjacent blade of the same set to provide a liquid passage therebetween, each set of blades within the casing chamber being spaced from its adjacent sets by unobstructed annular passageways adapted to receive annular bodies of fluid which during operation of the rotor extends unobstructed throughout 360, in each of said passageways, each annular passageway being of such radial depth between adjacent sets of blades that the annular body of fluid therein at the outer peripheral portion-will be centrifugally moved to- 4. A fluid pump comprising a stationary casing having a fluid chamber therein provided with an axial fluid inlet opening and an outer fluid delivery exit opening, a rotor supported by the casing having fixedly connected therewith an impeller structure comprising multiple blade setsall of which are disposed within said casing chamber and connected together for rotation in said chamber in the same direction, said blade sets all being located in the same plane normal to the axis of the rotor, each of said blade sets comprising a plurality of curved blades eccentrically disposed with respect to the center of rotation of the rotor upon centers located close to but spaced from the axis of the rotor to thereby provide shallow fluid throws for each blade, the blades of each set being so arranged that the outer end of each blade of each set is spaced from the inner end of an adjacent blade of the same set to provide a liquid passage therebetween, each set of blades within the chamber being definitely spaced from its adjacent sets of blades by unobstructed annular passageways provided to receive annular bodies of fluid which during operation of the rotor extends unobstructed throughout 360, each 6 of said annular passageways being of such radial depth between adjacent sets of blades that the annular body of fluid therein at the outer peripheral portion thereof will be centrifugally moved toward and shaved ofi continuously during operation of the rotor by the blades of the adjacent outermost set and thrown through the said liquid passages of said adjacent outermost set into the next outermost annular passageway.

WILLIAM C. HACKMAN.

REFERENCES CITED The following references are of record in the file of this patent:

I UNITED STATES PATENTS Number Name Date 862,017 Riggs July 30, 1907 877,484 Brooks Jan. 28, 1908 1,029,554 Neumayer June 11, 1912 1,225,805 Griepe May 15, 1917 2,042,064 Kugel May 26, 1936 2,165,808 Murphy July 11, 1939 FOREIGN PATENTS Number Country Date 28,218 Great Britain 1913 690,118 France Sept. 16, 1930 690,718 Germany May 4, 1940 

